KR19990067373A - Fluid cooling and gas dehumidification cooling method and apparatus - Google Patents

Abstract

The small permeation hole group 4 of the heat exchanger 3, which is an orthogonal flow type or an opposite flow type, is saturated with vapors of volatile liquids such as water and suspended in large quantities of fine particles of volatile liquids such as fine water in a fog state. The gas flow Aa is sent, and the fluid B to be cooled is passed through another small penetration hole group 5 so that the surface heat exchange is performed between the gas flow Aa and the fluid B, and the gas flow Aa. As the temperature rises, the fine particles of the volatile liquid floating in the gas flow Aa are vaporized and the fluid B is cooled by the vaporization.

When water is used as the fine particles of the volatile liquid suspended in the gas flow (Aa), a large amount of cold air can be supplied at a low cost, and the cooling temperature can be lowered by using a low boiling liquid such as methanol as the fine particles of the volatile liquid. .

Description

Fluid cooling and gas dehumidification cooling method and apparatus

In order to cool a gas or liquid, such as air, the refrigerator which generally liquefied volatile refrigerant | coolant, such as Freon, by the compressor and cooled by the heat of vaporization of the compressed Freon was conventionally used. In addition, in order to discharge the compressed heat of Freon, a cooling tower is used to cool Freund by passing the Freon through the spiral tube, flowing water in the spiral tube, and allowing air to flow in the opposite direction, and cooling by the heat of vaporization of the water. .

In general air conditioning, it is required to obtain air with a comfortable temperature and humidity, and when treating high temperature and humidity outside air, it is necessary to simultaneously lower the temperature and humidity. In the case of performing such air conditioning, the energy consumed for compressing the freon by the compressor is large, and the damage of the atmospheric ozone layer by the freon is a problem. And a large energy is consumed also in a cooling tower.

The present invention relates to a method and apparatus for cooling a fluid, for example air and air or a fluid by heat exchange of a liquid and gas, and a method and apparatus for dehumidifying and cooling a gas, for example air, as an application thereof.

BRIEF DESCRIPTION OF THE DRAWINGS Explanatory drawing which shows embodiment of the fluid cooling method and apparatus of this invention, and its enlarged part.

2 is a perspective view and a partially enlarged view showing an embodiment of a rectangular flow heat exchanger.

3 is a cross-sectional view showing another embodiment of the fluid cooling method and apparatus of the present invention.

4 is an explanatory diagram showing another embodiment of the method and apparatus for cooling a fluid of the present invention.

FIG. 5 is an air graph showing data of fluid cooling shown in FIG. 4.

6 is an explanatory diagram showing a control example of a fluid cooling method and apparatus.

FIG. 7 is an air graph showing data of the fluid cooling shown in FIG. 6.

8 is an explanatory diagram showing another embodiment of the method and apparatus for cooling a fluid of the present invention.

FIG. 9 is an air graph showing the fluid cooling data shown in FIG. 8.

10 is an explanatory diagram showing data of cooling using an aqueous methanol solution.

11 is an air graph showing data of cooling using an aqueous methanol solution.

12 is an explanatory diagram showing another embodiment of the method and apparatus for cooling a fluid of the present invention.

13 is a perspective view of the counterflow heat exchanger.

14 is a perspective view showing an embodiment of a heat exchanger in which an opposing flow and a cross flow are combined.

15 is a perspective view showing an embodiment according to the orthogonal flow type heat exchange.

16 is an explanatory diagram showing an embodiment of a gas dehumidification cooling method and apparatus of the present invention.

17 is an explanatory diagram showing another embodiment of the gas dehumidification cooling method and apparatus of the present invention.

18 is an explanatory view showing another embodiment of the gas dehumidification cooling method and apparatus of the present invention.

19 is a block diagram showing an embodiment of a cooling device of the refrigerator of the present invention.

20 is a perspective view showing an embodiment of a cooling apparatus of the refrigerator of the present invention.

21 is a block diagram showing another embodiment of the cooling device of the refrigerator of the present invention.

The present invention provides a method and apparatus for cooling a fluid, for example, a gas or a liquid, using a heat exchanger, and an air or low temperature / humidity having a comfortable temperature and humidity by dehumidifying and cooling a gas, for example, air. It is to supply gas continuously without using freon with little energy.

The present invention uses an orthogonal flow heat exchanger or a heat exchanger in which two kinds of fluids having different temperatures do not directly contact each other, thereby cooling the high temperature fluid B by surface heat exchange between the low temperature gas A and the hot gas B. Alternatively, the low temperature gas (A) is saturated with vapors of volatile liquids such as water vapor, and then a large amount of volatile liquids such as fine droplets are uniformly dispersed in a large amount, that is, a large amount of fine liquid droplets are suspended in the gas. The gas flow (Aa) in one state is transferred to the fluid passage on one side of the heat exchanger, and the hot gas B is sent to the fluid passage on the other side, and the above-described gas flow (through the heat exchanger by the surface heat of the fluid B) ( The liquid droplet M in Aa is evaporated to cool the gas Aa by the heat of evaporation, and the fluid B is cooled at a high efficiency by the heat exchange between the cooled gas flow Aa and the fluid B. To All.

The invention described in claim 1 of the present invention is a gas flow (Aa) in which a volatile liquid mist is added to the gas flow (A) to make it saturated, while the fine liquid droplet (M) in a mist state is suspended in a large amount. The gas flow Aa is passed through one of the fluid passages of the heat exchanger having a plurality of fluid passages, and the fluid B to be cooled through the other fluid passage is passed. As the surface heat of the fluid B is applied to the gas flow Aa while passing through the passage, the temperature of the gas flow Aa is raised to decrease the saturation of the gas portion (relative humidity if the volatile liquid is water). The liquid B is continuously cooled by continuously lowering the temperature of the gas flow Aa by the heat of vaporization which vaporizes a large amount of the fine liquid droplets M floating in the gas flow Aa. M) wealth in large quantities The gas flow Aa to be heated is heated by surface heat exchange with the fluid B in the fluid passage of the heat exchanger, and the vaporization heat caused by the vaporization of the fine liquid droplet M is deodorized, so that the temperature of the gas flow Aa is increased. Has a function of cooling down and cooling the fluid (B).

(Example 1)

A flat plate (1) made of a metal plate such as aluminum or a synthetic resin plate such as polyester and a wave plate (2) having a wavelength of 3.0 mm and a wave height of 1.6 mm are alternately bonded to each other so that the wave forms of the wave plate are orthogonal to each other. To form an orthogonal flow heat exchanger (3) as shown in FIG. In addition, when a small uneven portion is formed on the surface of the plate by blowing or the like, hydrophilicity is generated and the surface area is increased. To impart hydrophilicity to the aluminum sheet, hydrophilic substances are produced on the surface of the aluminum sheet by immersing the plate in an aqueous solution such as sodium phosphate, hypochlorite, chromic acid, phosphoric acid, hydroxide, or hydroxide, or briefly immersing it in boiling water. do. When the surface of the plate is made hydrophilic in this manner, when the fluid B is a gas such as air, it is possible to prevent the gas flowability from deteriorating in the small permeation hole due to the pressure drop caused by water droplets.

Although the combination of the flat plate 1 and the corrugated board 2 is illustrated as an orthogonal flow heat exchanger 3, when a fine corrugated form is formed in the flat plate 1 part, surface area will become large and heat exchange efficiency will increase. In addition, when the surfaces of the flat plate 1 and the corrugated plate 2 are blacked, the emission and absorption of radiant heat are increased to improve heat exchange efficiency.

As shown in Figs. 2 and 3, the small through hole group 4 on one side of the orthogonal flow type heat exchanger 3 is disposed almost vertically, and the other small through hole group 5 is substantially horizontal, As shown in Fig. 3, the ducts 8a and 8b are attached to the inlet 4a and the outlet 4b of the small through hole group 4, respectively, and the blower Fa and the water to the duct 8a. The sprayer 6 is provided, and the ducts 9a and 9b are attached to the inlet 5a and the outlet 5b of the small passage hole group 5 (FIG. 2), respectively, and the blower is attached to the duct 9a. Install F). In addition, reference numeral Va denotes a valve for adjusting the spray amount of the water sprayer 6.

It is preferable that the water sprayer 6 can distribute fine droplets as uniformly as possible, for example, an air mist nozzle or the like is suitable. In addition, water droplets should be as fine as possible and preferably about 10 μm in diameter, but when sprayed using an air mist nozzle, the water droplet diameter of about 70% is less than 100 μm when the maximum diameter of the water droplets is about 280 μm. Thus, the effects of the present invention are sufficiently exhibited.

In addition, the air mist nozzle is sprayed by using water and air, and when the water and air are pressurized, the spray droplets become small. In particular, the size of the spray droplets is susceptible to the influence of air pressure, and it is preferable to apply a pressure of 3 kgf / cm 2 or more. Moreover, you may use the nozzle which uses only a liquid.

Next, the operation of this cooling device will be described. As shown in Fig. 3, by using the above-described water sprayer 6 to the outside air or the indoor air flow A, the temperature is reduced by the heat of vaporization of the water droplets by spraying a large amount of fine water droplets on the air stream A. Lowers the relative humidity. Then, as the air flow Aa in which a large amount of fine water droplets M are suspended, it is sent to the plurality of fluid passage inlets 4a on one side of the heat exchanger 3 by the pressure of the blower Fa.

When the hot air flow B is sent to the fluid passage inlet 5a of the heat exchanger 3 by the other blower F, the air flow Aa passes through the fluid passage of the heat exchanger 3. The temperature of the air flow Aa is increased by deodorizing the surface heat of the hot air flow B through the partition wall 1 (see FIG. 2) of the fluid passage. As a result, the relative humidity of the air flow Aa is lowered, and a large amount of fine water droplets M contained in the air flow Aa vaporize, thereby lowering the temperature of the air flow Aa by this heat of vaporization. Cool the hot air stream (B) through (1).

The cooling principle of this cooling device is explained in more detail. The vapor pressure of the liquid is larger in the droplet state than in the state in which the liquid has a horizontal surface, and the smaller the diameter of the liquid droplet is, the larger it becomes. This phenomenon is expressed in Calvin as

log (pr / p) = 2δM / ρrRT

Where p is the vapor pressure of the horizontal surface, pr is the vapor pressure of the droplet of radius r, M is the molar mass, δ is the surface tension, ρ is the density of the liquid, R is the gas constant, and T is the absolute temperature.

Therefore, the smaller the radius of the droplets, the faster the vaporization and the stronger the cooling action. In addition, in the process of vaporizing the sprayed droplet M in the heat exchanger 3, since the diameter of the droplet M becomes small and a vapor pressure rises as the diameter of the droplet M becomes small, a heat exchanger In (3), vaporization of the water droplet M accelerates. That is, the fine water droplet M vaporizes in the heat exchanger 3 in a very short time, and deodorizes a large amount of heat of vaporization.

In the case of water at 18 ° C, when the radius of water droplets is 1 μ, the vapor pressure increases by 0.1% compared to when the water surface is parallel, and the radius of water droplets is 10 mμ. Vapor pressure rises about 10%. In addition, when the radius of the water droplets is 1 mμ, the vapor pressure almost doubles. When such fine water droplets M are suspended in a large amount of air to the heat exchanger 3, the water droplets M rapidly evaporate in the heat exchanger 3.

The test was performed using this chiller. As shown in FIG. 4, the airflow A having a temperature of 25.9 ° C., an absolute humidity of 8.05 g / kg, and a relative humidity of 39% is passed through the water sprayer 6 to lower the temperature to 17.5 ° C., and at the same time, a large amount of fine droplets. The air flow Aa of 100% of the relative humidity in which (M) is suspended is made, and this air flow Aa is connected to the inlet 4a of the small permeation hole group 4 which is arranged almost vertically of the heat exchanger 3. Send at a wind speed of 2m / sec. On the other hand, the inlet port 5a of the small permeation hole group where the high-temperature air flow B having a temperature of 70.6 ° C., an absolute humidity of 10.44 g / kg, and a relative humidity of 5.2% is arranged almost horizontally of the heat exchanger 3 by the blower F. ) At a wind speed of 2 m / sec. The small permeation hole group 4 may be permeated in a state where water droplets are suspended in the air even if they are not perpendicular to each other. 5 is an air graph showing air cooling in this case, and Table 1 shows the results of this test.

(With sprayer) Example 1 (when airflow B is high temperature) Temperature (℃) Absolute Humidity (g / kg) Relative Humidity (%) Airflow A 25.9 8.05 39 Airflow Aa 17.5 - 100 Airflow B 70.6 10.44 5.2 Supply air SA 18.6 10.44 78 Surface heat exchange efficiency η ₁ = (B-SA) / (B-Aa) × 100 = 97.9% (1)

Surface heat exchange is performed between the hot air stream B and the air flow Aa, thereby continuously lowering the temperature of the air flow Aa by vaporization of fine water droplets floating in the air flow Aa as described above. The airflow (B) is cooled and the temperature is lowered without raising the absolute humidity of the airflow (B) to make a comfortable air having a temperature of 18.6 ° C, an absolute humidity of 10.44 g / kg, and a relative humidity of 78% and use it as the supply air. The gas flow Aa becomes an air flow Ab having a temperature of 30.7 ° C. and a relative humidity of 100% through the heat exchanger 3. This air flow Ab is released to the atmosphere.

In this case, the surface heat exchange efficiency η ₁ is 97.9%, as shown in formula (1) in Table 1, and the heat exchange efficiency is very high. In formula, B, SA, and Aa represent each air temperature. In this case, the spray amount of the droplet M is approximately 8 to 15 liters per hour. In this case, the flow rates of the air flows A and B are about 180 m 3 / hour. The size of the heat exchanger is 0.25m × 0.25m = 0.0625m2, and the surface area of the inlets 4a and 5a is 0.625m2, respectively, and the open ratio of the holes is about 40%, so the cross-sectional area of the small through hole is 0.625m2 × 40 Since% = 0.025 m 2 and the wind speed is 2 m / sec, the air volume is 0.025 m 2 × 2 m / sec = 180 m 3 / hour.

As a comparative example for comparison with this, the test results when the water sprayer is not used for the cooling air flow using the same orthogonal flow type heat exchanger used in Example 1 are shown in FIG. 6 and Table 2 and FIG. Show in graph.

(No sprayer) Control Example (When Airflow B is High Temperature) Temperature (℃) Absolute Humidity (g / kg) Relative Humidity (%) Airflow A 22.3 7.58 45 Airflow B 67.2 11.34 7 Supply air Ba 36.0 11.34 31 Surface heat exchange efficiency η ₁ = (B-Ba) / (BA) × 100 = 69.5% (2)

In formula, B, Ba, and A represent each air temperature. The air flow A with a temperature of 22.3 ° C. becomes the air flow Ab with a temperature of 62.0 ° C. by surface heat exchange, and the high temperature air flow B with a temperature of 67.2 ° C. has an air flow Ba of temperature 36.0 ° C. by surface heat exchange. Becomes Absolute humidity does not change for both airflow (A) and airflow (B). In this case, the surface heat exchange efficiency η ₁ is 69.5% as shown in Equation (2) in Table 2. The surface heat exchange efficiency is 97.9% when water is sprayed, and the surface heat exchange efficiency is 69 when water is not sprayed. It becomes 5%, and about 30% heat exchange efficiency improves by spraying of water. In this case, other conditions are the same as in the case of spraying water of Example 1.

(Example 2)

Using this same cooling apparatus, as shown in Fig. 8, air having a temperature of 25.7 ° C, an absolute humidity of 12.20 g / kg, and a relative humidity of 59.0% is used as an air flow A of wind speed of 2 m / sec. Through the water sprayer 6, the air flow Aa is a temperature of 20.2 DEG C, a relative humidity of 100% and a large amount of fine water droplets in a mist state are uniformly suspended. The air flow Aa is a small through hole of the heat exchanger. It is sent to group 4 entrance 4a. On the other hand, hot air having a temperature of 34.2 DEG C, an absolute humidity of 14.41 g / kg, and a relative humidity of 43% as air to be cooled is used as the air flow B of a wind speed of 2 m / sec. Send to. The hot air flow B is subjected to surface heat exchange with the air flow Aa, so the air flow B is cooled air SA having a temperature of 20.6 ° C., an absolute humidity of 14.41 g / kg, and a relative humidity of 95%. The air flow Aa becomes an air flow Ab at a temperature of 25 ° C. and a relative humidity of approximately 100%, and the air flow Ab is released into the atmosphere. The air graph in this case is shown in FIG. 9, and a test result is shown in Table 3. FIG.

(With sprayer) Example 1 (when airflow (B) is room temperature) Temperature (℃) Absolute Humidity (g / kg) Relative Humidity (%) Airflow A 25.7 12.20 59.0 Airflow Aa 20.2 - 100 Airflow B 34.2 14.41 43 Supply air SA 20.6 14.41 95 Surface heat exchange efficiency η ₁ = (B-SA) / (BA) × 100 = 97.1% (3)

As shown, the heat of vaporization of the water droplets in the gas stream Aa is transferred to the gas flow B through the partition wall, so that the absolute humidity of the gas flow B does not change, as shown in the air graph, and the air graph. The temperature decreases along the horizontal line to reach the SA point (20.6 ° C), and the air flow (Aa) rises through the line of 100% relative humidity to the Ab point. In this case, the surface heat exchange efficiency is 97.1%, as shown in equation (3) in Table 3, which is almost the same as the surface heat exchange efficiency of Example 1. In other words, when the temperature of the fluid B decreases, the water spray amount may be reduced as long as the temperature of the supply air SA is 20.6 ° C., as long as it is suitable for air conditioning. The amount of water sprayed is about 8 l / hour.

(Example 3)

As shown in FIG. 1, the apparatus D of FIG. 3 described in Embodiment 1 receives a water droplet discharged along with the air flow Ab, a recirculation apparatus of water accumulated in the tank D, that is, a pump P, Electric valve (Va) and level control device (level level buoy (Vs), water level sensor (Se), electric valve (Vb), and spray amount control device of the water droplet spray device (6), thermocouple (Ta), thermocouple (Tb), The electric signal amplifier C and the electric valve Va are added. In the drawings, parts having the same numerals as those in FIG. 3 are the same as those described in FIG. 3 in the first embodiment, and thus description thereof is omitted.

The water pipe 10 which recirculates the water in the water tank D to the water sprayer 6 is attached, and the pump P and the electric valve Va are installed in the middle. In addition, a water supply pipe 11 is attached to the water tank D, and a water level buoy Vs is floated on the water surface 13 in the water tank D, and an on-off electromagnetic valve Vb and a water level sensor installed in the water supply pipe 11 are provided. By connecting (Se), as shown in the enlarged view of the Q portion of Figure 1, by measuring the change in the water level with the water level buoy (Vs) and the water level sensor (Se), if the water surface is lower than 13L, the electromagnetic valve (Vb) is Open the water supply, and if the water surface is higher than 13H, the electromagnetic valve (Vb) is closed to stop the water supply.

Upstream of the water sprayer 6, a temperature sensor of the gas flow A, for example a thermocouple Ta, and a temperature sensor, for example a thermocouple Tb, are arranged in the fluid B. (Ta), (Tb) is connected by sandwiching the electric signal amplifier (C). The temperature difference between the two thermocouples Ta and Tb is measured and sent to the electric signal amplifier C. As the temperature difference increases, the electric valve Va is operated to increase the amount of water sprayed, and as the temperature difference decreases, the amount of water sprayed. Decreases. If necessary, the air flow rate is accelerated by increasing the output of the blower Fa at the same time as the amount of water sprayed.

In this case, when the spraying amount in the water sprayer 6 is excessive, fine water droplets will collect on the inner wall surface of the small permeation hole group 4 of the heat exchanger 3, become a water flow, and fall into the water droplets without sufficient vaporization. This water flow has a very small surface area compared to the fine water droplets, and the amount of heat deodorized in the hot air flow (B) has little vaporization of water, and thus does not contribute to cooling. Therefore, the temperature of the gas flow Aa cannot be sufficiently lowered and the temperature of the hot air flow B cannot be lowered sufficiently. When the fine water droplets (M) in the air flow (Aa) are sprayed to the required amount uniformly, the cooling efficiency is increased and water can be saved.

(Example 4)

Volatile organic liquids such as ethanol (boiling point 78.3 ° C), methyl acetate (boiling point 56.3 ° C), methanol (boiling point 64.7 ° C), or volatile organic liquid and water, instead of water (boiling point 100 ° C) used in the atomizer 6 You may use a mixed liquid.

As shown in FIG. 2, fine particles of the absorbent silica gel are scattered and adhered to both surfaces of the partition wall 1 made of an aluminum plate having a thickness of 25 mu and the aluminum corrugated plate 2 having a wavelength of 3.4 mm and a height of 1.7 mm. These were alternately stacked to fabricate a crossflow heat exchanger of 250mm × 250mm × 250mm size. The cooling device shown in FIG. 10 was assembled using this heat exchanger 3, and the data at the time of using 45% aqueous methanol solution instead of the water used for the atomizer 6 in Example 1, 2 is shown in FIG. In this case, since an aqueous methanol solution was used instead of water, its boiling point was lowered, so that the air flow A having a temperature of 25.9 ° C. was lowered to a temperature of 14.6 ° C. after the spraying of the aqueous methanol solution (air flow Aa).

The low-temperature airflow SA of 17.2 ° C is obtained by heat exchange between 14.6 ° C of this airflow Aa and 51.3 ° C of the high-temperature airflow B. Therefore, low temperature air SA is obtained by spraying using a liquid having a boiling point lower than that of spraying only with water. The air graph of FIG. 11 is an air graph which shows the state change of the above-mentioned airflow B → SA and airflow A → Aa → Ab.

(Example 5)

In the apparatus of the present embodiment, as shown in Fig. 12, the apparatus described in Example 1 converts the gas flow Ab discharged from the outlet 4b of the heat exchanger 3 into a gas flow Aa of high humidity. A device for recirculating is added, and a humidifier 7 is provided on the upstream side of the water sprayer 6. In Fig. 12, the outlet 4b of the heat exchanger 3 and the blower Fc are connected to the duct 8e, and the fluid passage of the blower Fc and the gas flow Aa of high humidity is connected to the duct 8d. The branch duct K for suctioning the external air OA as necessary is connected to a part of the duct 8e.

The humidifier 7 is attached to the valve V in the middle of the water supply pipe Wp so that water can be supplied when it needs to be humidified. As the humidifier 7, there are used, for example, an ultrasonic type, a plurality of cloths which have been wetted with water, and the like.

The air flow Aa is passed through the heat exchanger 3, and the air flow Ab discharged from the outlet 4b is used as the gas flow Ac recycled by the blower Fc. This gas flow Ac passes through the humidifier 7 as needed and is recycled to the heat exchanger 3 as a gas flow Aa in which fine water droplets M are suspended in large quantities by a nebulizer.

In FIG. 12, the cooling part Co is provided in the middle of the duct 8e, many fins Fe are attached to the outer periphery of the duct 8e, and a cover is attached to this, and blower Fd is attached. The fluid Ab in the duct 8e is cooled by cooling the fin Fe by the blower Fd, and the moisture in the fluid Ab of high humidity is cooled and condensed. Da), and the water in the tank is sometimes discharged by the valve Vc and returned to the atomizer 6.

As mentioned above, although the fluid cooling method of this invention was demonstrated as an example of the air cooling method using a crossflow type heat exchanger, it is a matter of course that it is carried out similarly in the cooling of gas other than air or other liquid.

Instead of the orthogonal flow type described above, a heat exchanger in which a cross flow type, a counter flow type shown in FIG. 13, and a counter flow type and a cross flow type shown in FIG. 14 may be used may be used instead of the orthogonal flow type described above. In the heat exchanger in which the counter flow type shown in FIG. 13 and the counter flow type and the cross flow type shown in FIG. 14 are combined, the gas flow Aa in which fine water droplets are suspended together, and the fluid B are respectively indicated by arrows in the figure. It passes through the small through hole in the direction and is discharged as the gas flow Ab and the fluid SA, respectively, so that surface heat exchange is performed between the two fluids A and B. As shown in Fig. 15, an orthogonal flow heat exchanger in which a plurality of spacers 12 are sandwiched and assembled in a direction orthogonal to each stage between the flat plates 1 can be used. It is also possible to use a heat exchanger having the same counter flow type as the honeycomb laminate and a combination of the counter flow and the cross flow.

(Example 6)

As shown in FIG. 16, the 250 mm × 250 mm × 250 mm orthogonal flow heat exchanger 3 and the spray humidifier 6 are arranged to place the dehumidification rotor 14 at the front end of the heat exchanger 3. The dehumidification rotor 14 is formed by forming a honeycomb laminate in which an adsorbent or an absorbent is combined on a cylindrical shape having a diameter of 320 mm and a width of 200 mm. In addition, the dehumidification rotor 14 is separated into the adsorption zone 16 and the regeneration zone 17 by the separators 15 and 15 ', respectively, as indicated by arrows B → HA → SA by ducts (not shown), respectively. As shown, the fluid passage is configured, and the dehumidification rotor 14 is continuously rotated at 16 r.ph in the direction of the arrow in the figure. External air (OA) with a temperature of 34.0 ° C, an absolute humidity of 14.4 g / kg, and a relative humidity of 43.1% is taken as the air flow B by the blower Fb, and the adsorption zone of the dehumidification rotor 14 at a wind speed of 2 m / sec. Send to.

As a result, the moisture of the air stream B is adsorbed and removed to obtain a dry air stream HA. Next, the dry air flow HA is sent to the inlet 5a of the horizontal small penetration hole group 5 of the heat exchanger 3. In the regeneration zone 17 of the dehumidification rotor 14, the regeneration air RA heated by the heater H to about 80 ° C. in the direction of the arrow in the drawing is sent to the regeneration zone 17. The rotor 14 is dehumidified and regenerated and discharged into the outside air as humid exhaust air (EA).

On the other hand, when the temperature of the air flow A is humidified by the spray humidifier 6 while the relative humidity is 58% at 26 ° C, and the relative humidity is 100%, the temperature of the air flow Aa is 17.0 ° C. In addition, water is sprayed on the air flow Aa and sent to the inlet port 4a of the heat exchanger 3 in a state where fine droplets are floated innumerably.

The dry air flow HA passes through the heat exchanger 3 to perform surface heat exchange with the air flow Aa in which the fine droplets are floated innumerably, and as described in the first embodiment, the inside of the heat exchanger 3 It is cooled by the heat of vaporization of the fine water droplets of the air stream Aa to obtain a comfortable supply air SA having a temperature of 20.5 ° C., an absolute humidity of 4.5 g / kg, and a relative humidity of 30%.

As can be seen in this embodiment, the external air of absolute humidity of 14.4 g / kg and relative humidity of 43.1% is dehumidified to allow the heat exchanger 3 to pass dry air whose temperature rises and the humidity decreases due to the heat of adsorption of moisture. Thereby cooling dry air having a temperature of 20.5 ° C., an absolute humidity of 4.5 g / kg, and a relative humidity of 30%. When this air is used for air conditioning, it can be moderately humidified to provide a comfortable air condition.

As a dehumidifier, in addition to the rotary method used in this embodiment, two-cylinder, cylindrical, or casabar filled with an adsorbent (lithium chloride solution manufactured by Cassava, USA) is dropped into the container, and air is sent from the window on one side of the container to prevent moisture in the air. Dehumidifiers, such as a device which adsorb | suck to a lithium chloride solution) can also be used, of course.

(Example 7)

In this embodiment, the process of dehumidifying with a dehumidification rotor after cooling hot air of 70.0 ° C with a heat exchanger will be described.

As shown in FIG. 17, the spray humidifier 6 is disposed on the upper side of the orthogonal flow heat exchanger 3 to place the dehumidification rotor 14 at the rear end of the heat exchanger 3. When spraying water with the spray humidifier (6) to outside air (OA) of temperature 26.0 ° C., absolute humidity 12.2 g / kg, and relative humidity 58% through a blower Fa, the temperature is 17.5 ° C. Further, the air flow Aa in which a large amount of water fine particles are suspended by spraying water is passed through one of the fluid passages 4a of the heat exchanger 3.

On the other hand, the airflow B having a temperature of 70.0 ° C, an absolute humidity of 14.4 g / kg, and a relative humidity of 7% is sent by the blower Fb to the inlet 5a of the heat exchanger 3 at a wind speed of 2 m / sec. The air flow B is surface-heat-exchanged in a heat exchanger, resulting in a low temperature air flow Ba. The absolute humidity of the air flow Ba is almost the same as that of the air flow B. After the air flow Aa passes through the heat exchanger 3, the air flow Aa is discharged into the outside air at the outlet of the heat exchanger 3 as the air flow Ab at a temperature of 30.0 ° C and a relative humidity of about 100%. The dehumidification rotor 14 is rotated at 16 r.p.h. in the direction of the arrow in the figure.

The cooled air flow (Ba) is sent to the adsorption zone (16) of the dehumidification rotor 14, the moisture is adsorbed and removed to dry air flow (HA) with a temperature of 55 ℃, absolute humidity 4.5g / kg, relative humidity 5% Get The operation of the dehumidification rotor 14 is as described in the fifth embodiment. Dehumidification by adsorption from hot air is extremely difficult. However, as shown in the present embodiment, when the dehumidifier is used after cooling in a heat exchanger, dehumidification can be performed simply and effectively, and cooled dry air is obtained.

(Example 8)

The air flow (HA) obtained in Example 7 has a temperature of 55.0 ° C. and a relative humidity of 5%. The temperature is too high and the relative humidity is too low for general air conditioning. Therefore, the present embodiment is to pass the air flow (HA) further through the heat exchanger (3b) to obtain a supply air (SA) having a temperature and humidity suitable for air conditioning.

As shown in Fig. 18, the same hot air flow B as in Example 7 is passed through the orthogonal flow type heat exchanger 3a and the dehumidification rotor 14 to obtain the air flow HA. Since the operation so far is exactly the same as in the seventh embodiment, repeated explanation is omitted. The second orthogonal flow type heat exchanger (3b) is installed in the fluid passage of the rear end of the dehumidification rotor (14), that is, the air flow (HA) flowing out from the outlet of the process air, and the one fluid of the second heat exchanger (3b) is installed. The spray humidifier 6b similar to Example 7 is provided also at the upstream side of the passage 4. Since the operation of this second heat exchanger 3b is the same as that of the heat exchanger 3 of the seventh embodiment, the description thereof is omitted.

On the other hand, the dry air flow HA that has passed through the adsorption zone 16 of the dehumidification rotor 14 is sent to the fluid passage inlet 5a of the small permeation hole group 5 horizontally installed in the heat exchanger 3b. Surface heat exchange with a cooled air flow (Aa) containing fine droplets of water yields a comfortable supply air (SA) with a temperature of 20.5 ° C., an absolute humidity of 4.5 g / kg and a relative humidity of 30%. In the case of adjusting the air condition of the supply air SA, it is possible to change the temperature of the supply air SA by adding or subtracting the amount of water sprayed into the air flow Aa, and the temperature of the supply air SA is too high. If it is high, the lower the regeneration temperature of the dehumidification rotor lowers the dehumidification performance of the dehumidification rotor 14, it is possible to increase the humidity of the supply air (SA), it is possible to freely control the air.

In Examples 6 to 8 above, when the liquid having low boiling point, for example, ethanol, methyl acetate, methanol, or the like is sprayed on the air flow Aa instead of water used as the spray humidifier, the temperature of the supply air flow SA is increased. Can be lowered further.

In addition, in all embodiments, an ultrasonic mist forming apparatus can be used as the mist forming means. As the water atomizer, one fluid nozzle which does not use air other than the air mist nozzle can be used. In addition, in the above embodiment, while the relative humidity is set to 100% in the first stage of the spray humidifier and a large amount of water fine particles are suspended, a plurality of stages of the spray humidifier are installed to humidify the relative humidity to 100% in the initial stage. In the next step, it is advisable to float a large amount of water particles. In the end, the air having a large amount of water fine particles having a diameter of about 10 mu in a large amount of air in a relative humidity of 100% may be passed through the heat exchanger.

In the above embodiment, the heat exchanger is illustrated by alternately stacking the corrugated plate and the flat plate, but the present invention is not limited to this, and may be any one having a plurality of fluid passages and having a large surface area of the fluid passages. In addition, a fluid passage having a plurality of heat exchange fins may be provided at both ends of the heat pipe.

(Example 9)

In Fig. 19, reference numeral 18 denotes a known cooler and has a compressor (not shown) therein. Reference numeral 19 is a heat exchanger, one of the fluid passages 20 is a spiral tubular shape, and the other of the fluid passages 21 is a jacket surrounding the spiral tubular fluid passages 20. .

Refrigerant, such as high-temperature freon gas (chlorofluorohydrocarbon: a trademark of DuPont, USA), flows from one side of the heat exchanger 19 through the compressor, and the other fluid passage 21 of the heat exchanger 19 flows. Coolant flows through it.

The other fluid passage 21 of the heat exchanger 19 is connected to one of the fluid passages of the orthogonal flow heat exchanger 3 by fitting a pipe passage 22, and a recirculation pump 23 in the middle of the pipe passage 22. Is installed. That is, between the heat exchanger 19 and the orthogonal flow heat exchanger 3, the cooling water is recycled in a sealed state. Reference numerals 9a and 9b denote chambers.

Reference numeral Fa is a blower, the suction side is open to the atmosphere, and the discharge side is coupled with the upper end of the chamber 24. In addition, the lower end of the chamber 24 is thermally coupled with the inlet 4a of the other fluid passage of the orthogonal flow heat exchanger 3. The outlet of the other fluid passage of the orthogonal flow heat exchanger 3 is open to the atmosphere.

A spray device 6 is attached to the inside of the chamber 24, and the relative humidity of the air in the chamber 24 is 100%, and a large amount of fine water droplets is suspended, i.e., in a fog state. As the spraying device 6, an air spray nozzle is used, for example, and the water pressure pump P and the compressor 25 are connected.

Reference numeral D denotes a water tank receiving water, and is provided below the orthogonal flow heat exchanger 3, and a drain pipe 26 is provided.

As shown in Fig. 20, the axis of the small through-hole group 4 on one side of the orthogonal flow heat exchanger 3 is arranged approximately vertically, and the axis of the other small through-hole group 5 is approximately horizontal. The chamber 24 is attached to the inlet 4a of the penetrating hole group 4, and the blower Fa and the water sprayer 6 are attached to the chamber 24. As shown in FIG. Moreover, the chambers 9a and 9b are attached to the inlet 5a and the outlet 5b of the small penetration hole group 5, respectively, and the pipe 22 is connected to the chambers 9a and 9b.

The operation of the above configuration will be described below. First, the cooling means using the orthogonal flow heat exchanger 3 is demonstrated. The blower Fa is operated to produce a gas flow A, which is sprayed with a sprayer 6 to form a gas flow Aa. The amount of water to spray is more than the quantity to vaporize by spraying. Then, a part of sprayed droplets vaporize, the heat of vaporization by vaporization is deodorized, and the temperature of the gas flow Aa sent in the chamber 24 falls. In addition, the air in the chamber 24, that is, the gas flow Aa, has a relative humidity of 100%, whereby a large amount of water fine particles are suspended in the air, that is, a mist state.

In addition, air in a state in which the fine water droplets are suspended in a large amount enters the small permeation hole group 4 on one side of the orthogonal flow heat exchanger 3. When the refrigerator 18 is in an operating state, the temperature of the refrigerant sent to the fluid passage 20 on one side of the heat exchanger 19 becomes high, and the water sent to the other fluid passage 21 of the heat exchanger 19 is increased. Heat exchange.

The water sent to the other fluid passage 21 of the heat exchanger 19 is recycled by the pump 23 and the other side of the orthogonal flow heat exchanger 3 through the pipe 22 and the chamber 9a. It enters the small penetrating hole group 5. The partition wall 1 is sandwiched between one small through hole group 4 and the other small through hole group 5 to perform surface heat exchange. That is, the cooling water passing through the other small through hole group 5 is cooled by the gas flow Aa passing through the small through hole group 4 on one side, and at the same time, the small through hole group 4 on one side is cooled. The gas flow Aa passing through is heated.

Then, the relative humidity of the gas flow Aa passing through one of the small through hole groups 4 becomes 100% or less, and a large amount of water fine particles contained therein vaporize, and the heat of vaporization is deodorized and the gas flow Aa. Is cooled.

As a result, the temperature of the gas flow Aa passing through one of the small through hole groups 4 is kept substantially constant while being at a low temperature, so that the cooling water passing through the other small through hole group 5 is heat exchanged. It cools continuously over the whole area and the full width | variety of the small permeation | transmission hole group 5a of group 3, and this temperature is also maintained substantially constant.

In this case, if the amount of spray from the water spray device 6 is too large, fine water droplets gather on the partition walls in the small permeation hole group 4 of the orthogonal flow heat exchanger 3 to agglomerate, resulting in large droplets and water flow. As compared with the fine water droplets, the surface area of water and water flow is extremely small, and the amount of heat deodorized from the refrigerant cannot sufficiently lower the temperature of the gas flow Aa, and thus it is not possible to sufficiently lower the temperature of the refrigerant. Spraying so that the fine water droplets in the gas flow Aa are contained evenly more than the minimum required amount increases cooling efficiency and saves water.

Further, water droplets which do not vaporize in the small permeation hole group 4 of the orthogonal flow heat exchanger 3 accumulate in the water tank D receiving water and are discharged by the drain pipe 26. As described above, since the amount of water sprayed from the water spray device 6 is about the same as the amount of vaporization in the small perforation group 4 of the orthogonal flow type heat exchanger 3, it is accumulated in the tank D receiving the water. The amount of water is small, so it is not a problem even if it is disposed of entirely. Therefore, the water sprayed from the water sprayer 6 is used without being circulated, so that no water moss or the like is generated.

In the above embodiment, an example of using water as a liquid to be cooled has been described. However, in consideration of freezing in winter, 50% of an antifreezing agent such as ethylene glycol is added to the water to be cooled, and the heat exchanger 19 and the cross flow heat exchanger are added. In order to prevent corrosion of (3), addition of a corrosion inhibitor is also considered.

(Example 10)

Another embodiment of the chiller's chiller is shown in FIG. 21. Differences from that of the embodiment of FIG. 19 are described next. That is, in the ninth embodiment shown in FIG. 19, water is allowed to pass through the other small through-hole group 5 of the orthogonal flow type heat exchanger 3, but in the present embodiment, the orthogonal flow type heat exchanger 3 is used. The air flow from the blower (F) passes through the other small through hole group (5).

That is, reference numeral F is coupled to the inlet of the chamber 9a as a blower. The outlet of the chamber 9a is coupled to the inlet of the other small permeation hole group 5 of the orthogonal flow heat exchanger 3. The inlet of the chamber 9b is coupled to the outlet 5b of the small penetration hole group 5, and the outlet of the chamber 9b is coupled to the radiator 28.

In addition, a tube passage 27 is provided to allow the refrigerant from the refrigerator 18 to pass through the radiator 28. In addition, since the structure other than the difference mentioned above is the same as that of Example 9, description is abbreviate | omitted.

In the present embodiment, the air flows through the other small through-hole group 5 of the orthogonal flow heat exchanger 3 by the blower F, and is cooled in between to reach the radiator 28. The radiator 28 sends a high temperature refrigerant from the refrigerator 18 through the tube passage 27 to release heat of the refrigerant. The air passing through the small through hole group 5 is sent to the radiator 28.

That is, the radiator 28 is cooled by the airflow cooled through the other small through hole group 5 of the orthogonal flow heat exchanger 3, and is very efficient compared with being directly cooled by external air. Is improved.

In the applicant's experiment, the same flow as the orthogonal flow type heat exchanger 3 of Example 9 shown in FIG. 19 was used, and the orthogonal flow type heat exchanger 3 was applied at the external air temperature of 35 ° C. and the relative humidity of 39%. Air is sent from the blower Fa to the small permeation hole group 4 of) at a speed of 2 m / sec, and water of 12 L / hour is sprayed by the nebulizer 6. Then, the temperature of the air which enters the radiator 28 from the orthogonal flow heat exchanger 3 becomes 18.6 degreeC, and the cooling efficiency of a refrigerant | coolant becomes very high.

The thing of this embodiment can install the cooling apparatus of the refrigerator of this invention in front of the radiator of the air conditioning apparatus already installed, and can improve the efficiency of refrigerators, such as an air conditioning apparatus and a refrigerator which were already installed by simple construction.

Since the present invention is constituted as described above, the gas flow for cooling the mist gas flow Aa in which fine water droplets are uniformly suspended in a large quantity and 100% relative humidity in one fluid passage of the heat exchanger having a plurality of fluid passages. The gas flow Aa and the fluid B, which are passed through as a fluid and are passed through a partition wall and which are to be cooled in the other fluid passage, for example, air or water, and suspended fine droplets, are contacted through the partition wall and the gas flow Aa. It is a principle of lowering the relative humidity of the gas flow (Aa) by heating to evaporate fine water droplets to cool the gas flow (Aa) by the heat of evaporation, and at the same time to cool the fluid (B) through the partition wall. In the water sprayer, the degree of cooling the fluid B can be controlled by adding or subtracting the amount of water sprayed. Alternatively, when the water spray amount is increased as the temperature difference between the gas flow Aa and the hot air flow B increases, the fluid Aa cools the hot air stream B in proportion to the temperature difference of the hot air flow B. It becomes strong and can cool airflow B to a nearly constant comfortable temperature. In addition, by combining the cooling device and the dehumidifier, dry cooling air can be easily obtained.

As described in Example 1, the spray humidifier 6 is disposed in the orthogonal flow type heat exchanger 3, and the air flow Aa in which fine droplets are suspended in large quantities is used as the cooling air flow. The surface heat exchange efficiency when cooling is about 97% to 100%, which is very high. In the case of using the same orthogonal flow type heat exchanger used in Example 1 and not using the atomizer and the humidifier in the cooling air flow, the surface heat exchange efficiency is 63% as shown in Example 1 and the control example, and the present invention The heat exchange efficiency is found to be remarkably high in fluid cooling.

The energy required for this heat exchange is about 250 W of operating energy of the blower. On the other hand, the energy consumed for cooling the fluid B is, for example, 1.5 to several times the energy consumption. It rises as the temperature of (B) is high.

This fluid cooling device is used for gas cooling, and it can be used for dehumidification cooling of gas as shown in Examples 6-8 by adding a dehumidifier to this, and can be used as an air conditioner. In this case, since the cost required for operation is inexpensive as described above, for example, when used for dehumidification cooling in an enclosed room, there is no need to repeatedly use the indoor air, and fresh air is sucked in to remove the dehumidification cooling. You can continue. Therefore, it is possible to completely prevent the increase of harmful gases such as carbon dioxide in the indoor air, thereby providing a comfortable space.

In addition, since there is no use of freon as in conventional cooling, there is no environmental problem, there is no need to use a compressor, and there is no occurrence of bacteria or mold due to hot air of the discharged heat, so it has a very excellent effect in terms of hygiene.

Claims (30)

One fluid passage of the heat exchanger having a plurality of fluid passages, which is a gas flow (Aa) containing a volatile liquid vapor in the gas flow (A) in a saturated state and a large amount of fine droplets of mist (M) suspended therein. This gas flow (Aa) is passed through and gas (B) to be cooled in the other fluid passage, so that the gas flow (Aa) passes through one of the fluid passages of the heat exchanger. The surface heat of B) is applied to raise the temperature of the gas flow Aa, vaporizes a large amount of fine droplets M floating in the gas flow Aa, and continuously heats the temperature of the gas flow Aa by the heat of vaporization. Lowering and continuously cooling the fluid (B) by surface heat exchange of the gas flow (Aa) and the fluid (B). The method according to claim 1, characterized in that the floating amount of the fine droplet (M) in the gas flow (Aa) is changed in accordance with the change in the difference between the temperature of the gas flow (Aa) and the temperature of the fluid (B). Fluid cooling method. The method of claim 1, characterized in that the fine liquid droplet (M) is to change the flow rate of the floating gas flow (Aa) according to the change of the difference between the temperature of the gas flow (Aa) and the temperature of the fluid (B). Fluid cooling method. The gas droplet A according to any one of claims 1 to 3, wherein the gas flow A is a gas flow saturated with a vapor of a volatile liquid, and the mist of the volatile liquid is added to the gas flow to form a fine droplet (M). ) Is a gas flow (Aa) suspended in large quantities. 5. The gas flow Ab according to any one of claims 1 to 4 is returned to the inlet side of one passage of the heat exchanger by returning a gas flow Ab containing a large amount of volatile liquid vapor discharged from the outlet of one passage of the heat exchanger. A fluid cooling method characterized by using while circulating as a gas flow (Aa) in which fine droplets (M) are suspended by adding a mist of liquid. The fluid cooling method according to any one of claims 1 to 5, wherein the volatile liquid is water, a volatile organic liquid, or a mixed liquid of volatile organic liquid and water. The fluid cooling method according to any one of claims 1 to 6, wherein the volatile liquid is sprayed by a gas liquid mixed nozzle. The fluid cooling method according to any one of claims 1 to 7, wherein the diameter of the spray particle droplets is set to 280 µm or less. One of the fluids of the heat exchanger having a plurality of fluid passages is a gas flow (Aa) in which a volatile liquid mist is added to the gas flow (A) to make it saturated, and a large amount of fine droplets (M) in the mist state are suspended. Pass this gas stream (Aa) through the passage and pass the dry gas stream (B) dehumidified by the dehumidifier in the other fluid passage in advance, and between the gas flow (Aa) through the fluid passage on one side of the heat exchanger. The surface heat of the gas flow B is applied to the flow Aa to raise the temperature of the gas flow Aa, and the fine liquid droplets M floating in the gas flow Aa are vaporized and the gas flow is reduced by the heat of vaporization. Continuously raising the temperature of Aa), the gas flow (A) is cooled by the heat exchange of the gas flow (Aa) and the gas flow (B), the gas dehumidification cooling method characterized by continuously supplying the cooled dry gas . One of the fluids of the heat exchanger having a plurality of fluid passages is a gas flow (Aa) in which a volatile liquid mist is added to the gas flow (A) to make it saturated, and a large amount of fine droplets (M) in the mist state are suspended. This gas flow (Aa) passes through the passage and the gas flow (B) passes through the other fluid passage, and the gas flow (Aa) passes through the gas passage (Aa) between the gas passages (Aa) through the fluid passage of the heat exchanger. The surface heat of (B) is applied to increase the temperature of the gas flow Aa, vaporizes the fine droplet M floating in the gas flow Aa, and subsequently lowers this temperature by the heat of vaporization. Gas dehumidification by cooling the gas flow (B) by heat exchange of the gas flow (B), and then dehumidifying the cooled gas flow (Ba) through a dehumidifier to continuously supply the cooled dry gas. Cooling method. Two heat exchangers having a plurality of fluid passages and dehumidification means are used, and a fog of volatile liquid is added to the gas flow A passing through the two heat exchangers to saturate the liquid, and a large amount of fine droplets M in a mist state are obtained. This gas flow Aa is sent to one fluid passage of each of the two heat exchangers, and the other fluid passage, the dehumidification means, and the other of the second heat exchanger of the first heat exchanger are sent. The gas flow (B) is sequentially passed through the fluid passage, and the gas flow (B) and dehumidification in the gas flow (Aa) are passed between the gas flow (Aa) through the first fluid passage of the first and second heat exchangers. The surface heat of the high temperature and dry gas flow (HA) after dehumidification in Sudan raises the temperature of the gas flow (Aa), and the fine liquid droplets (M) suspended in the gas flow (Aa) are subjected to the hot gas flow (B), ( Vaporization by the surface heat of HA) and gas flow (Aa) by the heat of vaporization. And to lower the continuously dehumidifying gas cooling method which comprises continuously supplying a dried gas (SA) of the cold temperature. The volatile liquid mist is added to the gas flow A by means of the mist forming means of the volatile liquid, and the gas flow Aa in which the fine droplet M is suspended in saturation and in a large amount in a large amount is formed. The gas flow Aa is passed through one fluid passage of the heat exchanger having a passage and the fluid B to be cooled through the other fluid passage, and the gas flow Aa passes through the fluid passage of one of the heat exchangers. The gas flow Aa deodorizes the surface heat of the fluid B, vaporizes a large amount of fine droplets M floating in the gas flow Aa, and continuously heats the temperature of the gas flow Aa by the heat of vaporization. Fluid cooling apparatus characterized in that the fluid (B) is continuously cooled by lowering. 13. The fluid cooling device according to claim 12, wherein a means for introducing volatile liquid vapor is provided upstream of the mist forming means of the volatile liquid. 13. The cooling system according to claim 12, wherein the cooling gas flow Aa is circulated by installing a duct and a blower for directing the gas flow Ab discharged from one outlet of the heat exchanger to one inlet side of the heat exchanger. Fluid cooling device. 15. The heat exchanger of claim 12, wherein the heat exchanger is composed of a honeycomb laminate in which plate and corrugated plates are alternately stacked and is orthogonal, musk or opposite flow. A fluid cooling device comprising a heat exchanger combining a flow type and a cross flow type. 15. The heat exchanger according to any one of claims 12 to 14, wherein the heat exchanger is an orthogonal flow, a musk flow, or an opposite flow type in which a plate is laminated with a plurality of spacers interposed therebetween, or a combination of a counter flow type and a cross flow type. Fluid cooling device characterized in that. The fluid cooling device according to any one of claims 12 to 16, wherein the surface of the heat exchange element has hydrophilicity. The fluid cooling device according to any one of claims 15 to 16, wherein the fine particles are fixed to the fluid passage wall of the heat exchanger. 19. The fluid cooling device according to claim 18, wherein the fine particles are fine particles of the adsorbent. The volatile liquid mist is added to the gas flow A by means of the mist forming means of the volatile liquid, and the gas flow Aa in which the fine droplet M is suspended in saturation and in a large amount in a large amount is formed. A gas flow (Aa) is passed through one fluid passage of the heat exchanger having a passage and a hot gas flow (B) to be cooled into the other fluid passage is passed, and the gas flow (Aa) passes through one fluid passage of the heat exchanger. In the meantime, the gas flow Aa deodorizes the surface heat of the fluid B, vaporizes a large amount of fine droplets M floating in the gas flow Aa, and the temperature of the gas flow Aa by the heat of vaporization. And cooling the hot gas stream (B) continuously by continuously lowering the fluid cooling apparatus. The volatile liquid mist is added to the gas flow A by means of the mist forming means of the volatile liquid, and the gas flow Aa in which the fine droplet M is suspended in saturation and in a large amount in a large amount is formed. A gas flow (Aa) is passed through one fluid passage of the heat exchanger having a passage and a hot gas flow (B) to be cooled into the other fluid passage is passed, and the gas flow (Aa) passes through one fluid passage of the heat exchanger. In the meantime, the gas flow Aa deodorizes the surface heat of the high temperature gas flow B, vaporizes a large amount of fine droplets M floating in the gas flow Aa, and the gas flow Aa by the heat of vaporization. And continuously dehumidifying the hot gas flow (B) by continuously lowering the temperature of the gas, and a dehumidifying means is provided downstream from the above-mentioned hot gas flow (B) heat exchanger. The volatile liquid mist is added to the gas flow A by means of the mist forming means of the volatile liquid, and the gas flow Aa in which the fine droplet M is suspended in saturation and in a large amount in a large amount is formed. A gas flow (Aa) is passed through one fluid passage of the heat exchanger having a passage and a hot gas flow (B) to be cooled into the other fluid passage is passed, and the gas flow (Aa) passes through one fluid passage of the heat exchanger. In the meantime, the gas flow Aa deodorizes the surface heat of the high temperature gas flow B, vaporizes a large amount of fine droplets M floating in the gas flow Aa, and the gas flow Aa by the heat of vaporization. Two gas cooling means for continuously cooling the hot gas flow B by continuously lowering the temperature of the gas are provided, and dehumidifying means are provided between the flows of the hot gas flow B in the above two cooling means. Characterized by Gas dehumidification cooling device. The gas dehumidification cooling apparatus according to any one of claims 20 to 22, wherein a means for introducing volatile liquid vapor is provided upstream of the volatile liquid atomizer. 23. The gas flow in the cooling fog state according to any one of claims 20 to 22, wherein a duct and a blower are provided to guide the gas flow Ab discharged from one outlet of the heat exchanger to one inlet side of the heat exchanger. Gas dehumidification cooling device characterized in that the. 25. The heat exchanger of claim 20, wherein the heat exchanger consists of a honeycomb laminate in which plate and corrugated plates are alternately stacked and is orthogonal, musk or opposite flow type. Gas dehumidification cooling device characterized in that the heat exchanger combined the flow type and cross-flow type. The heat exchanger according to any one of claims 20 to 24, wherein the heat exchanger is an orthogonal, a musk flow, or an opposite flow type in which a plate is laminated with a plurality of spacers interposed therebetween, or a combination of a counter flow type and a cross flow type. Gas dehumidification cooling device characterized in that the heat exchanger. In cooling a heat exchanged fluid with a heat source of a refrigerator, it has a heat exchanger having a passage of two fluids which exchange heat with each other, and in the gas stream saturated with volatile liquid vapor in a gas flow, Spray until the fine droplets are in a floating state to make the gas flow in the fog state, and at the same time, the gas flow flows through one of the passages of the heat exchanger, and the heat exchanger is heated by the vaporization heat of the droplets in the heat exchanger. Cooling apparatus of the freezer, characterized in that for cooling the cooled fluid passing through the other side of the passage. In cooling the fluid to be heat exchanged with the source of the refrigerator, it has a heat exchanger having passages of two fluids which exchange heat with each other, saturates the gas stream with vapor of volatile liquid, Spray until the droplets become suspended and make the gas flow in the mist state, while flowing the gas flow in one of the passages of the heat exchanger, and the vaporized heat of the droplets in the heat exchanger. A chiller cooling device, characterized in that for cooling the cooled fluid passing through the other side of the passage of the heat exchanger. 29. The cooling apparatus according to claim 27 or 28, wherein the cooled fluid is water or a mixed liquid with water. 29. The cooling apparatus according to claim 27 or 28, wherein the fluid to be cooled is a gas.